US20220145886A1 - Dry pump for gas and set of a plurality of dry pumps for gas - Google Patents
Dry pump for gas and set of a plurality of dry pumps for gas Download PDFInfo
- Publication number
- US20220145886A1 US20220145886A1 US17/439,018 US201917439018A US2022145886A1 US 20220145886 A1 US20220145886 A1 US 20220145886A1 US 201917439018 A US201917439018 A US 201917439018A US 2022145886 A1 US2022145886 A1 US 2022145886A1
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- screw
- rotor
- dry pump
- screws
- lobe
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- 239000007789 gas Substances 0.000 claims abstract description 49
- 230000000903 blocking effect Effects 0.000 claims description 9
- 238000004891 communication Methods 0.000 claims description 2
- 230000006835 compression Effects 0.000 description 20
- 238000007906 compression Methods 0.000 description 20
- 238000011144 upstream manufacturing Methods 0.000 description 5
- 238000010438 heat treatment Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 239000000470 constituent Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/005—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of dissimilar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/082—Details specially related to intermeshing engagement type pumps
- F04C18/084—Toothed wheels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/126—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
- F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2220/00—Application
- F04C2220/10—Vacuum
- F04C2220/12—Dry running
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/20—Rotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/30—Casings or housings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2250/00—Geometry
- F04C2250/20—Geometry of the rotor
Definitions
- the present invention relates to the field of pumping and the compression of gases. More specifically, it concerns a dry pump for gases as well as a set of a plurality of dry pumps for gases.
- a screw pump comprises two screws which mesh and which are driven in opposite directions, each on one of two parallel axes of rotation.
- each screw belongs to a rotor, which further comprises a lobe portion, in such a way that the screw pump and a lobe pump are thus combined, as is the case, for example, in the American patent U.S. Pat. No. 7,611,340 B2.
- the threadings of the screws can vary along the screws, to define an internal compression rate of the gas between the upstream end of the screws and their downstream end.
- the threadings of the screws can vary by means of a progressive or stepwise change of the pitch of each thread.
- the number of turns of the threads along the screw can be changed, that is to say the length of the screws can be changed, in order to modify the dynamic “tightness” and thus the final pressure or the final vacuum obtained by the screw pump.
- a modification of the compression rate requires a new form of screw to be achieved, for each screw, while, in the screw pumps, the shape of the screws of variable threading is very complex and thus very difficult to design and to machine.
- the invention has at least as an object to simplify the design and/or the creation of a range of dry pumps for gases having different compression rates. More specifically, the invention has as an object to create a range of dry pumps for gases proposing, for the same or similar constraints with respect to bulkiness, energy consumption, etc., the flexibility and advantages of a variable pitch screw pump, but having rotors with a profile easier to design and/or to machine.
- a dry pump for gases comprising a first rotor comprising a first lobe portion and a first screw, a second rotor comprising a second lobe portion and a second screw, as well as a casing in which the first and second rotors are mounted for rotation in such a way that the first and second screws mesh and that the first and second lobe portions engage one with the other.
- the casing delimits an internal volume in which the first and the second screws and the first and the second lobe portions are located together. At least one inlet comes out into the internal volume at the first and second lobe portions. At least one outlet of the internal volume is located opposite the inlet in relation to the first and second screws.
- Each of the first and second screws comprises a threading invariable along its length.
- the first and second rotors are rotational in opposite directions in such a way as to be able to be located successively in:
- the first and second screws have as a role to block and to open the chamber.
- the first and second lobe portions have as a role to carry out the compression.
- the first and second screws can thus not have as a role to carry out a compression, and the threading of each of them is invariable on its length. For this reason, these first and second screws are not difficult to design, nor to produce, compared with screws of variable threading.
- the compression rate is a function of the first and second lobe portions. This compression rate can be modified by playing with the dimension of the first and second lobe portions in the axial direction. Starting with a given first screw and a given second screw, pumps not having the same compression rates can thus be constructed, depending on the axial dimension of the lobe portions that are associated with these first and second screws. Moreover, the lobe portions are much less difficult to produce than the screws.
- the dry pump for gases defined above can incorporate one or more other advantageous features, alone or in combination, in particular from among those defined in the following.
- the first and second lobe portions comprise lobes each of which extends by one of the helical threads of the threadings of the first and second screws.
- the number of lobes of the first lobe portion is equal to the number of helical threads of the threading of the first screw, the number of lobes of the second lobe portion being equal to the number of helical threads of the threading of the second screw.
- the outlet is located at a distance from the first and second screws.
- the chamber is one of a plurality of successive chambers that the first and second rotors and the casing together delimit.
- one of the successive chambers is a collecting chamber which has the outlet from the internal volume.
- the threading of the first screw and the threading of the second screw delimit helical grooves, the downstream ends of these helical grooves being open and coming out into the collecting chamber regardless of the angular positions of the first and second rotors.
- the first and second screws do not carry out any compression.
- the heating of the gas because of its compression occurs essentially at the first and second lobe portions. For that reason, it is easier to prevent a big increase in the temperature of the first and second screws in operation and thus to prevent significant deformations in these first and second screws owing to expansions.
- one of the successive chambers is an intake chamber which communicates with the inlet.
- the first rotor is a male rotor, the second rotor being a female rotor.
- the second rotor comprises one more lobe than the first rotor.
- the first rotor comprises a plurality of lobes which number two, the second rotor comprising a plurality of lobes which number three.
- the first rotor has a cross section which is the same at the first lobe portion and at the first screw, apart from its angular orientation
- the second rotor has a cross section which is the same at the second lobe portion and at the second screw, apart from its angular orientation
- the first rotor comprises at least two monobloc elements, kept together, which are a first monobloc element comprising at least the first screw and a second monobloc element comprising at least one part of the first lobe portion.
- the invention also has as subject matter a set of a plurality of dry pumps for gases such as defined previously.
- the first screws of a first dry pump for gases of the set and of a second dry pump for gases of the set are identical, the second screws of the first dry pump for gases and of the second dry pump for gases being identical, the first and second lobe portions of the first dry pump for gases having an axial dimension which is a first axial dimension, the first and second lobe portions of the second dry pump for gases having an axial dimension which is a second axial dimension different from the first axial dimension.
- FIG. 1 is a schematic view and axial section of a dry pump for gases according to one embodiment of the invention
- FIG. 2 is a view in perspective which represents two constituent rotors of the pump of FIG. 1 and which is simplified in that the shafts of these rotors are omitted;
- FIG. 3 is a lateral and exploded view, which represents a single one of the two rotors of the pump of FIG. 1 and which is simplified in that the shaft of the rotor represented is omitted;
- FIG. 4 is a view which is simplified like FIGS. 2 and 3 , which represents the same rotors as FIG. 2 , as well as chambers partially delimited by these rotors in the pump of FIG. 1 , and where the rotors are seen from one end;
- FIG. 5 is a view in perspective which is simplified like FIGS. 2 and 3 and which represents the same rotors as FIG. 2 , as well as chambers partially delimited by these rotors in the pump of FIG. 1 ;
- FIG. 6 is a view in perspective representing one chamber from among the chambers visible in FIGS. 4 and 5 ;
- FIG. 7 is a view in perspective which represents the same chamber as FIG. 6 but later, that is to say at a moment after the moment at which this chamber is such as represented in FIG. 6 ;
- FIG. 8 is a view in perspective which represents the same chamber as FIGS. 6 and 7 but later, that is to say at a moment after that moment at which this chamber is such as represented in FIG. 7 ;
- FIG. 9 is a graph which represents the evolution of the capacity of the chamber of FIGS. 6 to 8 in the course of time.
- a dry pump for gases comprises a first rotor 1 and a second rotor 2 , which are mounted in a casing 3 in several parts kept assembled.
- a plurality of bearings 5 support a shaft 6 of the first rotor 1 in such a way that this first rotor 1 is rotational on an axis of rotation X 1 -X′ 1 .
- a plurality of bearings 7 support a shaft 8 of the second rotor 2 in such a way that this second rotor 2 is rotational on an axis of rotation X 2 -X′ 2 parallel to the axis of rotation X 1 -X′ 1 .
- the axial direction is the direction parallel to the axes of rotation X 1 -X′ 1 , and X 2 -X′ 2
- an axial dimension is a dimension in the direction parallel to the axes of rotation X 1 -X′ 1 , and X 2 -X′ 2 .
- One end of the shaft 8 is coupled to a motor 10 for driving the first and second rotors 1 and 2 .
- the shaft 8 of the second rotor 2 bears a toothed wheel 11 which meshes with a toothed wheel 12 borne by the shaft 6 of the first rotor 1 .
- the toothed wheels 11 and 12 form a gearing whose gear ratio equal to 3/2 is such that the first rotor 1 turns faster than the second rotor 2 .
- the first rotor 1 comprises a first lobe portion 1 A and a first screw 1 B which follow one another axially without distance between them.
- the second rotor 2 comprises a second lobe portion 2 A and a second screw 2 B which follow one another axially without distance between them.
- the first lobe portion 1 A, the first screw 1 B, the second lobe portion 2 A and the second screw 2 B are all in a same internal volume 14 , which the casing 3 delimits without compartmentalizing it.
- An inlet 15 for gas intake passes through the casing 3 and comes out into the internal volume 14 , at the first and second lobe portions 2 A and 2 B, of one side of the plane passing through the axes of rotation X 1 -X′ 1 and X 2 -X′ 2 .
- An outlet 16 for the discharge of gases passes through the casing 3 and communicates with the internal volume 14 , at a collecting chamber 18 , which is constituted by a downstream portion of this internal volume 14 and which is located at the outlet of the first and second screws 1 B and 2 B, that is to say opposite the first and second lobe portions 1 A and 2 A in relation to these first and second screws 1 B and 2 B.
- the internal volume 14 is cylindrical at least at the first and second screws 1 B and 2 B, by being constituted by the union of two interpenetrating cylinders of revolution, the respective axes of which are the axes of rotation X 1 -X′ 1 and X 2 -X′ 2 .
- the internal volume 14 is cylindrical in an identical way, at least on the side opposite the inlet 15 in relation to the plane containing the axes of rotation X 1 -X′ 1 and X 2 -X′ 2 .
- a downstream and lateral portion of the internal volume 14 can constitute an intake chamber where the internal volume 14 is enlarged laterally and where the inlet 15 comes out.
- the reference numerals 17 designate devices, each of which achieves a tightness between the casing 3 and one of the shafts 6 and 8 .
- the first rotor 1 is a male rotor.
- the first lobe portion 1 A comprises a plurality of lobes 20 which are identical and which number two in the embodiment represented.
- the screw 1 B comprises a threading made up of as many helical threads 21 as there are lobes 20 . This threading is invariable on the entire length of the screw 1 B. Its pitch, its average diameter and its profile, that is to say the shape and the dimensions of its section along an axial plane passing through the axis of rotation X 1 -X′ 1 , are invariable on the entire length of the screw 1 B.
- Each lobe 20 is extended by one of the two helical threads 21 , which are identical.
- the number of lobes 20 can be different from two. The same applies to the number of helical threads 21 .
- the second rotor 2 is a female rotor.
- the second lobe portion 2 A comprises a plurality of lobes 22 which are identical and which number three in the embodiment represented.
- the screw 2 B comprises a threading made up of as many helical threads 23 as there are lobes 22 . This threading is invariable on the entire length of the screw 2 B. Its pitch, its average diameter and its profile, that is to say the shape and the dimensions its section along an axial plane passing through the axis of rotation X 2 -X′ 2 , are invariable on the entire length of the screw 2 B.
- Each lobe 22 is extended by one of the three helical threads 23 , which are identical.
- the number of lobes 22 can be different from two. The same applies to the number helical threads 23 .
- the first lobe portion 1 A meshes with the second lobe portion 2 A.
- the first and second screws 1 B and 2 B interlock.
- the first rotor 1 has a cross section which is the same at the first lobe portion 1 A and at the first screw 1 B, apart from its angular orientation.
- the second rotor 2 has a cross section which is the same at the second lobe portion 2 A and at the second screw 2 B, apart from its angular orientation.
- the first rotor 1 results from the assembly of a plurality of monobloc elements, of which a first comprises the first lobe portion 1 A and of which a second comprises the first screw 1 B.
- the shaft 6 can be part of the first monobloc element of the first rotor 1 or of the second monobloc element of the first rotor 1 .
- a third monobloc element of the first rotor 1 can constitute the shaft 6 .
- the second rotor 2 results from the assembly of a plurality of monobloc elements, of which a first comprises the second lobe portion 2 A and of which a second comprises the second screw 2 B.
- the shaft 8 can be part of either of the first and second monobloc elements of the second rotor 2 .
- a monobloc element distinct from the first and second monobloc elements of the second rotor 2 can constitute the shaft 8 .
- the first rotor 1 , the second rotor 2 and the casing 3 delimit jointly a plurality of successive chambers which are visible in FIG. 4 , for certain ones, and in FIG. 5 , for all.
- these successive chambers are the collecting chamber 18 , the intake chamber mentioned above and designated by reference numeral 25 in FIGS. 4 and 5 , as well as the chambers 30 , 31 , 32 and 33 .
- FIGS. 4 and 5 When the first and second rotors 1 and 2 are located in the configuration represented in FIGS. 4 and 5 , the chambers 30 , 31 , 32 and 33 are closed. When the dry pump for gases of FIG. 1 operates, the first and second rotors 1 turn in opposite directions, as indicated by the arrows in FIG. 4 . Therefore the chambers 30 , 31 , 32 and 33 evolve, which is illustrated by FIGS. 6 to 8 , representing the single chamber 30 at successive moments.
- the chamber 30 is as shown in FIG. 6 .
- the chamber 30 is as shown in FIG. 7 .
- the chamber 30 has the shape and the position which the chamber 31 has in FIGS. 3 and 4 .
- the chamber 30 is as shown in FIG. 8 .
- the chamber 30 has the shape and the position which the chamber 32 has in FIGS. 3 and 4 .
- the chamber 30 is closed by being blocked, at its downstream end, that is to say at P 1 , by the intersection of a helical thread 21 and a helical thread 23 . Still in FIG. 6 , the first and second lobe portions 1 A and 2 A, a portion of the first screw 1 B, a portion of the second screw 2 B and the casing 3 together delimit the chamber 30 , which has almost reached its maximum capacity.
- first and second lobe portions 1 A and 2 A arrive at a configuration starting from which they together reduce the capacity of the chamber 30 of which the downstream end is still blocked at P 1 by the intersection of a helical thread 21 and a helical thread 23 .
- the chamber 30 is represented at a selected moment while the first and second lobe portions 1 A and 2 A reduce together the capacity of the chamber 30 .
- a compression of the gas present in this chamber 30 occurs.
- the compression in the chamber 30 is followed by a blocking of the upstream end of this chamber 30 , by the intersection of a helical thread 21 and a helical thread 23 .
- the chamber 30 is as shown in FIG. 8 .
- the blocking of the upstream end of the chamber 30 is located at P 2 in this FIG. 8 .
- the continuation of the rotations of the first and second rotors 1 and 2 in opposite directions causes the chamber 30 to be displaced in axial direction, downstream, but without changing capacity. In other words, there is no compression in the chamber 30 after the blocking at P 2 has taken place.
- the curve C in FIG. 9 is the graphic representation of the capacity V of the chamber 30 as a function of time t.
- the role of the first and second screws 1 B and 2 B is not to bring about a reduction of the capacity and thus a compression.
- the first and second screws have as their role to carry out a succession of identical blockages at the blocking point at P 1 , which retains gas when, in the chamber 30 , this gas is compressed by the first and second lobe portions 1 A and 2 A.
- the first and second screws also have as a role to carry out a succession of identical blockages at the blocking point at P 2 , which isolates the gas present in the chamber 30 of the first and second lobe portions 1 A and 2 A after the compression of this gas.
- the heating up due to this compression occurs also essentially at the first and second lobe portions 1 A and 2 A. Thanks to this, a low temperature rise of the first and second screws 1 B and 2 B can be obtained, bringing about an efficient cooling of the internal volume 14 at the first and second lobe portions 1 A and 2 A. Moreover, a low temperature rise of the first and second screws 1 B and 2 B is advantageous insofar as it is rather complicated to master the consequences of expansions in screws owing to the fact that such screws have complex shapes.
Abstract
Description
- The present invention relates to the field of pumping and the compression of gases. More specifically, it concerns a dry pump for gases as well as a set of a plurality of dry pumps for gases.
- One type of dry pump for gases is the screw pump. A screw pump comprises two screws which mesh and which are driven in opposite directions, each on one of two parallel axes of rotation. In the case of certain mixed pumps, each screw belongs to a rotor, which further comprises a lobe portion, in such a way that the screw pump and a lobe pump are thus combined, as is the case, for example, in the American patent U.S. Pat. No. 7,611,340 B2.
- In a screw pump, the threadings of the screws can vary along the screws, to define an internal compression rate of the gas between the upstream end of the screws and their downstream end. For example, the threadings of the screws can vary by means of a progressive or stepwise change of the pitch of each thread. Still in a screw pump, the number of turns of the threads along the screw can be changed, that is to say the length of the screws can be changed, in order to modify the dynamic “tightness” and thus the final pressure or the final vacuum obtained by the screw pump. In any case, a modification of the compression rate requires a new form of screw to be achieved, for each screw, while, in the screw pumps, the shape of the screws of variable threading is very complex and thus very difficult to design and to machine.
- To modify the nominal flow rate of a screw pump, keeping the same speed of rotation and the same spacing, modified can be the pitch of the threads at the upstream end of the screws and/or the bottom diameters of the threads and consequently the crest diameters of the threads (the thread profile height). These modifications must remain within the limits of mechanical stability in rotation as well as within the possibilities of industrial machining. In any case, a change of the nominal flow requires a new form of screw to be achieved, for each screw, while, in the screw pumps, the shape of the screw of variable threading is very complex and thus very difficult to design and to machine.
- The invention has at least as an object to simplify the design and/or the creation of a range of dry pumps for gases having different compression rates. More specifically, the invention has as an object to create a range of dry pumps for gases proposing, for the same or similar constraints with respect to bulkiness, energy consumption, etc., the flexibility and advantages of a variable pitch screw pump, but having rotors with a profile easier to design and/or to machine.
- According to the invention, this object is achieved by means of a dry pump for gases comprising a first rotor comprising a first lobe portion and a first screw, a second rotor comprising a second lobe portion and a second screw, as well as a casing in which the first and second rotors are mounted for rotation in such a way that the first and second screws mesh and that the first and second lobe portions engage one with the other. The casing delimits an internal volume in which the first and the second screws and the first and the second lobe portions are located together. At least one inlet comes out into the internal volume at the first and second lobe portions. At least one outlet of the internal volume is located opposite the inlet in relation to the first and second screws. Each of the first and second screws comprises a threading invariable along its length. The first and second rotors are rotational in opposite directions in such a way as to be able to be located successively in:
-
- a first configuration in which the first and second lobe portions, a portion of the first screw, a portion of the second screw and the casing together delimit a chamber which is closed,
- a second configuration in which the chamber is always delimited by the first and second lobe portions, a portion of the first screw, a portion of the second screw and the casing in such a way as to be closed and have a smaller capacity than in the first configuration,
- a third configuration in which the chamber is displaced entirely at the first and second screws and isolated from the lobe portions at least by a helical thread of the threading of the first screw, a helical thread of the threading of the second screw and a blocking made by an intersection of the helical thread of the first screw and of the helical thread of the second screw, and
- a fourth configuration in which the chamber is displaced at the downstream end of the first and second screws and is in communication with the outlet.
- The first and second screws have as a role to block and to open the chamber. The first and second lobe portions have as a role to carry out the compression. The first and second screws can thus not have as a role to carry out a compression, and the threading of each of them is invariable on its length. For this reason, these first and second screws are not difficult to design, nor to produce, compared with screws of variable threading.
- Furthermore, the compression rate is a function of the first and second lobe portions. This compression rate can be modified by playing with the dimension of the first and second lobe portions in the axial direction. Starting with a given first screw and a given second screw, pumps not having the same compression rates can thus be constructed, depending on the axial dimension of the lobe portions that are associated with these first and second screws. Moreover, the lobe portions are much less difficult to produce than the screws.
- Thus, a range of dry pumps for gases having different compression rates can be designed and produced more easily thanks to the invention.
- The dry pump for gases defined above can incorporate one or more other advantageous features, alone or in combination, in particular from among those defined in the following.
- Preferably, the first and second lobe portions comprise lobes each of which extends by one of the helical threads of the threadings of the first and second screws.
- Preferably, the number of lobes of the first lobe portion is equal to the number of helical threads of the threading of the first screw, the number of lobes of the second lobe portion being equal to the number of helical threads of the threading of the second screw.
- Preferably, the outlet is located at a distance from the first and second screws.
- Preferably, the chamber is one of a plurality of successive chambers that the first and second rotors and the casing together delimit.
- Preferably, regardless of the respective angular positions of the first and second rotors, there are always two closed chambers among the successive chambers.
- Preferably, one of the successive chambers is a collecting chamber which has the outlet from the internal volume.
- Preferably, the threading of the first screw and the threading of the second screw delimit helical grooves, the downstream ends of these helical grooves being open and coming out into the collecting chamber regardless of the angular positions of the first and second rotors. When such is the case, the first and second screws do not carry out any compression. The heating of the gas because of its compression occurs essentially at the first and second lobe portions. For that reason, it is easier to prevent a big increase in the temperature of the first and second screws in operation and thus to prevent significant deformations in these first and second screws owing to expansions.
- Preferably, one of the successive chambers is an intake chamber which communicates with the inlet.
- Preferably, the first rotor is a male rotor, the second rotor being a female rotor.
- Preferably, the second rotor comprises one more lobe than the first rotor.
- Preferably, the first rotor comprises a plurality of lobes which number two, the second rotor comprising a plurality of lobes which number three.
- Preferably, the first rotor has a cross section which is the same at the first lobe portion and at the first screw, apart from its angular orientation, while the second rotor has a cross section which is the same at the second lobe portion and at the second screw, apart from its angular orientation.
- Preferably, the first rotor comprises at least two monobloc elements, kept together, which are a first monobloc element comprising at least the first screw and a second monobloc element comprising at least one part of the first lobe portion.
- The invention also has as subject matter a set of a plurality of dry pumps for gases such as defined previously. The first screws of a first dry pump for gases of the set and of a second dry pump for gases of the set are identical, the second screws of the first dry pump for gases and of the second dry pump for gases being identical, the first and second lobe portions of the first dry pump for gases having an axial dimension which is a first axial dimension, the first and second lobe portions of the second dry pump for gases having an axial dimension which is a second axial dimension different from the first axial dimension.
- Other advantages and features will emerge more clearly from the description which follows of a particular embodiment of the invention, given by way of non-limiting example, and represented in the annexed drawings of which:
-
FIG. 1 is a schematic view and axial section of a dry pump for gases according to one embodiment of the invention; -
FIG. 2 is a view in perspective which represents two constituent rotors of the pump ofFIG. 1 and which is simplified in that the shafts of these rotors are omitted; -
FIG. 3 is a lateral and exploded view, which represents a single one of the two rotors of the pump ofFIG. 1 and which is simplified in that the shaft of the rotor represented is omitted; -
FIG. 4 is a view which is simplified likeFIGS. 2 and 3 , which represents the same rotors asFIG. 2 , as well as chambers partially delimited by these rotors in the pump ofFIG. 1 , and where the rotors are seen from one end; -
FIG. 5 is a view in perspective which is simplified likeFIGS. 2 and 3 and which represents the same rotors asFIG. 2 , as well as chambers partially delimited by these rotors in the pump ofFIG. 1 ; -
FIG. 6 is a view in perspective representing one chamber from among the chambers visible inFIGS. 4 and 5 ; -
FIG. 7 is a view in perspective which represents the same chamber asFIG. 6 but later, that is to say at a moment after the moment at which this chamber is such as represented inFIG. 6 ; -
FIG. 8 is a view in perspective which represents the same chamber asFIGS. 6 and 7 but later, that is to say at a moment after that moment at which this chamber is such as represented inFIG. 7 ; and -
FIG. 9 is a graph which represents the evolution of the capacity of the chamber ofFIGS. 6 to 8 in the course of time. - In
FIG. 1 , a dry pump for gases according to one embodiment of the invention comprises afirst rotor 1 and asecond rotor 2, which are mounted in a casing 3 in several parts kept assembled. - A plurality of
bearings 5 support a shaft 6 of thefirst rotor 1 in such a way that thisfirst rotor 1 is rotational on an axis of rotation X1-X′1. A plurality ofbearings 7 support ashaft 8 of thesecond rotor 2 in such a way that thissecond rotor 2 is rotational on an axis of rotation X2-X′2 parallel to the axis of rotation X1-X′1. In the sense intended here and in the annexed claims, the axial direction is the direction parallel to the axes of rotation X1-X′1, and X2-X′2, while an axial dimension is a dimension in the direction parallel to the axes of rotation X1-X′1, and X2-X′2. - One end of the
shaft 8 is coupled to amotor 10 for driving the first andsecond rotors motor 10, theshaft 8 of thesecond rotor 2 bears atoothed wheel 11 which meshes with atoothed wheel 12 borne by the shaft 6 of thefirst rotor 1. Thetoothed wheels first rotor 1 turns faster than thesecond rotor 2. - The
first rotor 1 comprises afirst lobe portion 1A and afirst screw 1B which follow one another axially without distance between them. Thesecond rotor 2 comprises asecond lobe portion 2A and asecond screw 2B which follow one another axially without distance between them. Thefirst lobe portion 1A, thefirst screw 1B, thesecond lobe portion 2A and thesecond screw 2B are all in a sameinternal volume 14, which the casing 3 delimits without compartmentalizing it. - An
inlet 15 for gas intake passes through the casing 3 and comes out into theinternal volume 14, at the first andsecond lobe portions outlet 16 for the discharge of gases passes through the casing 3 and communicates with theinternal volume 14, at a collectingchamber 18, which is constituted by a downstream portion of thisinternal volume 14 and which is located at the outlet of the first andsecond screws second lobe portions second screws - The
internal volume 14 is cylindrical at least at the first andsecond screws second lobe portions internal volume 14 is cylindrical in an identical way, at least on the side opposite theinlet 15 in relation to the plane containing the axes of rotation X1-X′1 and X2-X′2. At theinlet 15, a downstream and lateral portion of theinternal volume 14 can constitute an intake chamber where theinternal volume 14 is enlarged laterally and where theinlet 15 comes out. - The reference numerals 17 designate devices, each of which achieves a tightness between the casing 3 and one of the
shafts 6 and 8. - As can be seen in
FIG. 2 , thefirst rotor 1 is a male rotor. Thefirst lobe portion 1A comprises a plurality oflobes 20 which are identical and which number two in the embodiment represented. Thescrew 1B comprises a threading made up of as manyhelical threads 21 as there arelobes 20. This threading is invariable on the entire length of thescrew 1B. Its pitch, its average diameter and its profile, that is to say the shape and the dimensions of its section along an axial plane passing through the axis of rotation X1-X′1, are invariable on the entire length of thescrew 1B. Eachlobe 20 is extended by one of the twohelical threads 21, which are identical. The number oflobes 20 can be different from two. The same applies to the number ofhelical threads 21. - The
second rotor 2 is a female rotor. Thesecond lobe portion 2A comprises a plurality oflobes 22 which are identical and which number three in the embodiment represented. Thescrew 2B comprises a threading made up of as manyhelical threads 23 as there arelobes 22. This threading is invariable on the entire length of thescrew 2B. Its pitch, its average diameter and its profile, that is to say the shape and the dimensions its section along an axial plane passing through the axis of rotation X2-X′2, are invariable on the entire length of thescrew 2B. Eachlobe 22 is extended by one of the threehelical threads 23, which are identical. The number oflobes 22 can be different from two. The same applies to the numberhelical threads 23. - The
first lobe portion 1A meshes with thesecond lobe portion 2A. The first andsecond screws - The
first rotor 1 has a cross section which is the same at thefirst lobe portion 1A and at thefirst screw 1B, apart from its angular orientation. In an identical way, thesecond rotor 2 has a cross section which is the same at thesecond lobe portion 2A and at thesecond screw 2B, apart from its angular orientation. - As can be seen well in
FIG. 3 , thefirst rotor 1 results from the assembly of a plurality of monobloc elements, of which a first comprises thefirst lobe portion 1A and of which a second comprises thefirst screw 1B. The shaft 6 can be part of the first monobloc element of thefirst rotor 1 or of the second monobloc element of thefirst rotor 1. Likewise, a third monobloc element of thefirst rotor 1 can constitute the shaft 6. Thesecond rotor 2 results from the assembly of a plurality of monobloc elements, of which a first comprises thesecond lobe portion 2A and of which a second comprises thesecond screw 2B. Theshaft 8 can be part of either of the first and second monobloc elements of thesecond rotor 2. Likewise, a monobloc element distinct from the first and second monobloc elements of thesecond rotor 2 can constitute theshaft 8. - At all times, the
first rotor 1, thesecond rotor 2 and the casing 3 delimit jointly a plurality of successive chambers which are visible inFIG. 4 , for certain ones, and inFIG. 5 , for all. Among these successive chambers are the collectingchamber 18, the intake chamber mentioned above and designated byreference numeral 25 inFIGS. 4 and 5 , as well as thechambers - When the first and
second rotors FIGS. 4 and 5 , thechambers FIG. 1 operates, the first andsecond rotors 1 turn in opposite directions, as indicated by the arrows inFIG. 4 . Therefore thechambers FIGS. 6 to 8 , representing thesingle chamber 30 at successive moments. - When the first and
second rotors FIGS. 4 and 5 , thechamber 30 is as shown inFIG. 6 . After thefirst rotor 1 and thesecond rotor 2 have turned respectively by half a turn and by a third of a turn starting from positions which they have inFIGS. 3 and 4 , thechamber 30 is as shown inFIG. 7 . When it is as shown inFIG. 7 , thechamber 30 has the shape and the position which thechamber 31 has inFIGS. 3 and 4 . After thefirst rotor 1 and thesecond rotor 2 have turned respectively by one turn and by 2/3 of a turn starting from the positions that they have inFIGS. 3 and 4 , thechamber 30 is as shown inFIG. 8 . When it is as shown inFIG. 8 , thechamber 30 has the shape and the position which thechamber 32 has inFIGS. 3 and 4 . - Described now will be the evolution of the
chamber 30 in the course of time, while the first and second rotors turn continuously in opposite directions. - In
FIG. 6 , thechamber 30 is closed by being blocked, at its downstream end, that is to say at P1, by the intersection of ahelical thread 21 and ahelical thread 23. Still inFIG. 6 , the first andsecond lobe portions first screw 1B, a portion of thesecond screw 2B and the casing 3 together delimit thechamber 30, which has almost reached its maximum capacity. - The rotations of the first and
second rotors FIGS. 4 and 5 . Therefore, the first andsecond lobe portions chamber 30 of which the downstream end is still blocked at P1 by the intersection of ahelical thread 21 and ahelical thread 23. InFIG. 7 , thechamber 30 is represented at a selected moment while the first andsecond lobe portions chamber 30. At the same time that the first andsecond lobe portions chamber 30, a compression of the gas present in thischamber 30 occurs. - While the rotations of the first and
second rotors chamber 30 is followed by a blocking of the upstream end of thischamber 30, by the intersection of ahelical thread 21 and ahelical thread 23. After the blocking of its upstream end occurs, thechamber 30 is as shown inFIG. 8 . The blocking of the upstream end of thechamber 30 is located at P2 in thisFIG. 8 . - Once the blocking at P2 occurs, the continuation of the rotations of the first and
second rotors chamber 30 to be displaced in axial direction, downstream, but without changing capacity. In other words, there is no compression in thechamber 30 after the blocking at P2 has taken place. - When the
chamber 30 reaches the downstream end of the first andsecond screws chamber 30, since theoutlet 16 is at a distance from the first andsecond screws - The curve C in
FIG. 9 is the graphic representation of the capacity V of thechamber 30 as a function of time t. - It can be seen from the foregoing that the role of the first and
second screws chamber 30, this gas is compressed by the first andsecond lobe portions chamber 30 of the first andsecond lobe portions - As the compression has taken place essentially at the first and
second lobe portions second lobe portions second screws internal volume 14 at the first andsecond lobe portions second screws
Claims (14)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/EP2019/056501 WO2020182317A1 (en) | 2019-03-14 | 2019-03-14 | Dry pump for gas and set of a plurality of dry pumps for gas |
Publications (2)
Publication Number | Publication Date |
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US20220145886A1 true US20220145886A1 (en) | 2022-05-12 |
US11920592B2 US11920592B2 (en) | 2024-03-05 |
Family
ID=65904380
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US17/439,018 Active 2039-08-15 US11920592B2 (en) | 2019-03-14 | 2019-03-14 | Dry pump for gas and set of a plurality of dry pumps for gas |
Country Status (10)
Country | Link |
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US (1) | US11920592B2 (en) |
EP (1) | EP3938657B1 (en) |
JP (1) | JP7315693B2 (en) |
KR (1) | KR102583846B1 (en) |
CN (1) | CN113544384B (en) |
AU (1) | AU2019433234A1 (en) |
CA (1) | CA3128596A1 (en) |
ES (1) | ES2951988T3 (en) |
PL (1) | PL3938657T3 (en) |
WO (1) | WO2020182317A1 (en) |
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CN107084135A (en) * | 2017-06-29 | 2017-08-22 | 德耐尔节能科技(上海)股份有限公司 | A kind of dry-type spiral vacuum pump |
-
2019
- 2019-03-14 JP JP2021554379A patent/JP7315693B2/en active Active
- 2019-03-14 US US17/439,018 patent/US11920592B2/en active Active
- 2019-03-14 AU AU2019433234A patent/AU2019433234A1/en active Pending
- 2019-03-14 ES ES19712929T patent/ES2951988T3/en active Active
- 2019-03-14 KR KR1020217033262A patent/KR102583846B1/en active IP Right Grant
- 2019-03-14 WO PCT/EP2019/056501 patent/WO2020182317A1/en active Application Filing
- 2019-03-14 EP EP19712929.9A patent/EP3938657B1/en active Active
- 2019-03-14 CN CN201980093824.9A patent/CN113544384B/en active Active
- 2019-03-14 PL PL19712929.9T patent/PL3938657T3/en unknown
- 2019-03-14 CA CA3128596A patent/CA3128596A1/en active Pending
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Also Published As
Publication number | Publication date |
---|---|
CN113544384A (en) | 2021-10-22 |
PL3938657T3 (en) | 2023-10-16 |
KR102583846B1 (en) | 2023-09-27 |
CN113544384B (en) | 2023-09-08 |
AU2019433234A1 (en) | 2021-09-16 |
EP3938657B1 (en) | 2023-06-07 |
EP3938657A1 (en) | 2022-01-19 |
EP3938657C0 (en) | 2023-06-07 |
ES2951988T3 (en) | 2023-10-26 |
JP7315693B2 (en) | 2023-07-26 |
CA3128596A1 (en) | 2020-09-17 |
US11920592B2 (en) | 2024-03-05 |
KR20210135328A (en) | 2021-11-12 |
TW202100868A (en) | 2021-01-01 |
WO2020182317A1 (en) | 2020-09-17 |
JP2022525448A (en) | 2022-05-16 |
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